WO2020067195A1 - 多段圧縮システム - Google Patents

多段圧縮システム Download PDF

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Publication number
WO2020067195A1
WO2020067195A1 PCT/JP2019/037670 JP2019037670W WO2020067195A1 WO 2020067195 A1 WO2020067195 A1 WO 2020067195A1 JP 2019037670 W JP2019037670 W JP 2019037670W WO 2020067195 A1 WO2020067195 A1 WO 2020067195A1
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WO
WIPO (PCT)
Prior art keywords
oil
container
refrigerant
stage
stage compressor
Prior art date
Application number
PCT/JP2019/037670
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大輔 岡本
梶原　幹央
洋平 西出
直人 富岡
将彬 足立
洋輔 大西
明敏 上野
堀田　卓也
竹上　雅章
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to CN201980063044.XA priority Critical patent/CN112771322A/zh
Priority to EP19866259.5A priority patent/EP3835685B1/de
Priority to ES19866259T priority patent/ES2939052T3/es
Priority to US17/277,687 priority patent/US11428225B2/en
Publication of WO2020067195A1 publication Critical patent/WO2020067195A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/806—Pipes for fluids; Fittings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Definitions

  • a multi-stage compression mechanism using a plurality of compressors is recommended and used.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2008-2612257
  • An oil drain passage and an oil return passage for returning oil discharged on the high-stage side to the suction pipe of the low-stage compressor are provided.
  • Patent Document 1 oil discharged from the high-stage compressor is returned to the suction side of the accumulator in front of the low-stage compressor.
  • the hole for oil return provided in the suction pipe in the accumulator generally has a small hole diameter. Therefore, even if an oil return pipe is connected to the suction side of the accumulator, it is difficult to quickly increase the oil amount of the low-stage compressor.
  • the multi-stage compression system of the first aspect utilizes a refrigerant and oil.
  • the multi-stage compression system has a low-stage compressor, a high-stage compressor, an oil return pipe, and an oil discharge pipe.
  • the low-stage compressor compresses the refrigerant.
  • the high-stage compressor further compresses the refrigerant compressed by the low-stage compressor.
  • the oil return pipe returns oil discharged from the high-stage compressor or oil in the high-stage compressor to the low-stage compressor.
  • the oil discharge pipe discharges the oil of the low-stage compressor.
  • the low-stage compressor has a compression section, a motor, and a container.
  • the compression section compresses the refrigerant.
  • the motor drives the compression unit.
  • the container houses the compression unit and the motor.
  • An oil return pipe and an oil discharge pipe are connected to the container.
  • the oil return pipe is connected to the container, the response of the oil return is quick, and the oil amount of the low-stage compressor can be easily increased. Further, since the oil discharge pipe is also connected to the container, more rapid control of the oil amount can be realized.
  • a multi-stage compression system is the system according to the first aspect, wherein the motor is disposed above the compression section.
  • the multi-stage compression system according to the third aspect is the system according to the first aspect or the second aspect, wherein the oil return pipe and the oil discharge pipe are connected to a container above the compression unit and below the motor.
  • the compression section is, specifically, a compression chamber.
  • the compression chamber referred to here means the lowest compression chamber.
  • the oil return pipe is connected to a position above the compression section of the container and below the motor, so that oil can be supplied more quickly to the oil pool of the low-stage compressor. it can. Further, since the oil discharge pipe is connected to a position above the compression section of the container and below the motor, excess oil of the low-stage compressor can be discharged from the low-stage compressor without excess or shortage.
  • a multi-stage compression system is the system according to any one of the first to third aspects, wherein a height of a connection position of the oil return pipe to the container is a height of a connection position of the oil discharge pipe to the container. Higher than
  • the oil level of the oil reservoir of the low-stage compressor is appropriately controlled.
  • a multi-stage compression system is the system according to any one of the first to third aspects, wherein a height of a connection position of the oil return pipe to the container is a height of a connection position of the oil discharge pipe to the container.
  • the oil level in the oil reservoir of the low-stage compressor is suppressed so as not to rise too much, and the oil amount of the low-stage compressor is appropriately controlled.
  • a multi-stage compression system is the system according to any one of the first to fifth aspects, wherein a connection position of the oil discharge pipe to the container is determined from a connection position of the oil return pipe to the container in a top view. , 90 ° or more apart in the rotation direction of the motor.
  • the oil introduced into the vessel of the low-stage compressor by the oil return pipe is directly discharged out of the vessel by the oil discharge pipe. And reduce oil pressure in low-stage compressors.
  • a multi-stage compression system is the system according to the sixth aspect, wherein a connection position of the oil discharge pipe to the container is 180 ° or more away from a connection position of the oil return pipe to the container in a rotation direction of the motor. Position.
  • the multi-stage compression system according to the seventh aspect reduces the oil that is introduced into the container of the low-stage compressor through the oil return pipe and is discharged from the container as it is through the oil discharge pipe.
  • the multi-stage compression system is the system according to any one of the first to seventh aspects, wherein a compression chamber is formed in the compression section.
  • a refrigerant is introduced and compressed.
  • the compression section has a muffler.
  • a discharge hole is formed in the muffler. The discharge hole discharges the refrigerant compressed in the compression chamber.
  • the connection position of the oil discharge pipe to the container is a position opposite to the discharge hole of the muffler with respect to the center of rotation of the motor.
  • the opposite position means a range of 180 ° other than a total of 180 ° of 90 ° left and right with respect to the center of rotation from the connection position of the oil discharge pipe.
  • connection position of the oil discharge pipe to the container is far from the position of the discharge hole of the muffler, so that the refrigerant discharged from the discharge hole of the muffler is directly subjected to low-stage compression by the discharge pipe. Emission from the machine can be reduced.
  • the multistage compression system according to the ninth aspect is the system according to any of the first to eighth aspects, wherein the diameter of the oil discharge pipe is equal to the diameter of the oil return pipe.
  • the multi-stage compression system of the ninth aspect since the diameters of the oil discharge pipe and the oil return pipe are equal, it is easy to adjust the oil return amount and the oil discharge amount equally, and the low-stage compressor can be easily oil-equalized. it can.
  • a multi-stage compression system is the system according to any one of the first to ninth aspects, wherein the refrigerant is a refrigerant mainly containing carbon dioxide, and the oil is an oil incompatible with carbon dioxide. is there.
  • the refrigerant and the oil are incompatible, the refrigerant and the oil are easily separated, and the oil is mainly introduced into the low-stage compressor or the refrigerant is mainly discharged from the low-stage compressor. Or easy to do.
  • FIG. 2 is a refrigerant circuit diagram of the refrigeration apparatus 1 according to the first embodiment.
  • FIG. 2 is a longitudinal sectional view of the low-stage compressor 21 of the first embodiment.
  • BB sectional view of the low-stage compressor 21 of the first embodiment CC sectional view of the low-stage compressor 21 of the first embodiment
  • FIG. 1 shows a refrigerant circuit configuration of the refrigerating apparatus 1 of the first embodiment.
  • the refrigeration apparatus 1 of the present embodiment is an apparatus that performs a two-stage compression refrigeration cycle using carbon dioxide that is a refrigerant that operates in a supercritical region.
  • the refrigerating device 1 of the present embodiment can be used for an air conditioner for cooling and heating, an air conditioner for cooling only, a chiller / heater, a refrigeration device, a freezing storage device, and the like.
  • the refrigerant circuit of the refrigeration apparatus 1 of the present embodiment includes a multi-stage compression system 20, a four-way switching valve 5, a heat source side heat exchanger 2, a bridge circuit 3, expansion mechanisms 8 and 9, and a use side heat exchanger 4 And an economizer heat exchanger 7.
  • the multi-stage compression system 20 compresses the refrigerant.
  • the gas refrigerant is introduced into the first accumulator 22 at the inlet of the low-stage compressor 21 via the four-way switching valve 5 and the refrigerant pipe 13.
  • the refrigerant is compressed by the low-stage compressor 21 and the high-stage compressor 23, and reaches the four-way switching valve 5 via the pipe 18.
  • the four-way switching valve 5 switches the direction of the flow of the refrigerant from the multistage compression system 20 to the heat source side heat exchanger 2 or the use side heat exchanger 4.
  • the refrigeration apparatus 1 is an air conditioner and performs a cooling operation
  • the refrigerant flows from the four-way switching valve 5 to the heat source side heat exchanger 2 (condenser).
  • the refrigerant flowing through the heat source side heat exchanger 2 (condenser) reaches the receiver 6 via the check valve 3a, the pipe 11, and the check valve 11e of the bridge circuit 3.
  • the liquid refrigerant from the receiver 6 continues to flow through the pipe 11, is decompressed by the expansion mechanism 9, and goes to the use-side heat exchanger 4 (evaporator) via the check valve 3 c of the bridge circuit 3.
  • the refrigerant heated by the use-side heat exchanger 4 (evaporator) is compressed again by the multi-stage compression system 20 via the four-way switching valve 5.
  • the refrigerant flows from the four-way switching valve 5 to the use side heat exchanger 4 (condenser), the check valve 3b of the bridge circuit 3, the pipe 11, the receiver 6, the expansion mechanism 9, and the reverse of the bridge circuit 3. It flows in the order of the stop valve 3d, the use side heat exchanger 4 (evaporator), and the four-way switching valve 5.
  • the economizer heat exchanger 7 is arranged in the refrigerant pipe 11 between the receiver 6 and the expansion mechanism 9. At the branch 11 a of the pipe 11, a part of the refrigerant branches and is reduced to an intermediate pressure by the expansion mechanism 8.
  • the intermediate-pressure refrigerant is heated by the high-pressure refrigerant flowing through the pipe 11 in the economizer heat exchanger 7, and is injected via the intermediate injection pipe 12 into the intermediate-pressure merging portion 15 b of the multistage compression system 20.
  • the gas component of the refrigerant flows from the receiver 6 via the pipe 19 to the intermediate injection pipe 12.
  • the multistage compression system 20 of the present embodiment includes a first accumulator 22, a low stage compressor 21, an intercooler 26, A second accumulator 24, a high-stage compressor 23, an oil separator 25, an oil cooler 27, and a pressure reducer 31a are provided.
  • the refrigerant compressed by the low-stage compressor 21 is further compressed by the high-stage compressor 23.
  • the compressors 21 and 23 include accumulators 22 and 24, respectively.
  • the accumulators 22, 24 serve to temporarily store the refrigerant before entering the compressor and prevent liquid refrigerant from being sucked into the compressor.
  • the low-pressure gas refrigerant heated by the evaporator flows to the first accumulator 22 via the refrigerant pipe 13.
  • the gas refrigerant in the first accumulator 22 flows to the low-stage compressor 21 via the suction pipe 14.
  • the refrigerant compressed by the low-stage compressor 21 is discharged from the discharge pipe 15a, flows through the intermediate-pressure refrigerant pipe 15, and reaches the second accumulator 24.
  • the intercooler 26 is arranged in the middle of the intermediate-pressure refrigerant pipe 15.
  • the intercooler 26 is a heat exchanger that cools the intermediate-pressure refrigerant with, for example, outdoor air.
  • the intercooler 26 may be arranged adjacent to the heat source side heat exchanger 2 and exchange heat with air by a common fan.
  • the intercooler 26 increases the efficiency of the refrigeration system 1 by cooling the intermediate-pressure refrigerant.
  • the intermediate pressure refrigerant is injected from the intermediate injection pipe 12 into the junction 15b of the intermediate pressure refrigerant pipe 15.
  • the junction 15b of the intermediate injection pipe 12 with the pipe 15 is disposed downstream of the intercooler 26.
  • the temperature of the refrigerant injected by the intermediate injection is lower than the temperature of the refrigerant flowing through the pipe 15. Therefore, the intermediate injection lowers the temperature of the refrigerant flowing through the pipe 15 and improves the efficiency of the refrigeration system 1.
  • the multi-stage compression system 20 of the present embodiment further includes an oil discharge pipe 32 that discharges excess oil of the low-stage compressor 21.
  • the oil discharge pipe 32 connects the low-stage compressor 21 and the intermediate-pressure pipe 15.
  • the oil discharge pipe 32 discharges not only excess oil accumulated in the oil sump of the low-stage compressor 21 but also excess refrigerant accumulated in the oil sump.
  • the connection part of the oil discharge pipe 32 with the intermediate-pressure refrigerant pipe 15 is a part downstream of the intercooler 26 and the junction part 15b of the intermediate injection pipe.
  • the refrigerant sent to the second accumulator 24 by the pipe 15 is introduced into the high-stage compressor 23 through the suction pipe 16.
  • the refrigerant is compressed in the high-stage compressor 23 to have a high pressure, and is discharged to the discharge pipe 17.
  • the refrigerant discharged to the discharge pipe 17 flows to the oil separator 25.
  • the oil separator 25 separates the refrigerant and the oil.
  • the separated oil is returned to the low-stage compressor 21 via the oil return pipe 31.
  • the multi-stage compression system 20 of the present embodiment further includes an oil discharge pipe 33 that discharges excess oil of the high-stage compressor 23.
  • the oil discharge pipe 33 connects the high-stage compressor 23 and the discharge pipe 17 of the high-stage compressor 23.
  • a pressure reducer 31a is arranged in the middle of the oil return pipe 31.
  • the pressure reducer 31a is for reducing the pressure of the high-pressure oil discharged from the oil separator 25.
  • a capillary tube is used as the decompressor 31a.
  • An oil cooler 27 is arranged in the oil return pipe 31.
  • the oil cooler 27 is a heat exchanger that cools the oil flowing through the oil return pipe 31 with, for example, outdoor air.
  • the oil cooler 27 is for cooling the high-temperature oil discharged from the oil separator 25.
  • the oil cooler 27 may be arranged, for example, in the vicinity of the heat source side heat exchanger 2 and exchange heat with air using a common fan.
  • the oil of the present embodiment (the refrigerating machine oil), if the refrigerating machine oil used in the CO 2 refrigerant is not particularly limited, CO 2 refrigerant and incompatible oils are particularly suitable.
  • the refrigerator oil include PAG (polyalkylene glycols) and POE (polyol esters).
  • the refrigerating apparatus 1 of the present embodiment performs two-stage compression using two compressors. Two or more stages of compression may be performed using three or more compressors. Further, three or more stages of compression may be performed.
  • the low-stage compressor 21 and the high-stage compressor 23 of the present embodiment are both two-cylinder type and oscillating rotary compressors. is there. Since the compressors 21 and 23 have almost the same configuration, a detailed description will be given using the low-stage compressor 21 here.
  • FIG. 2 is a longitudinal sectional view of the low-stage compressor 21, and FIGS. 3 to 5 are horizontal sectional views at positions AA to CC in FIG. However, the section of the motor 40 is not shown in the BB sectional view of FIG.
  • the low-stage compressor 21 includes the container 30, the compression section 50, the motor 40, the crankshaft 60, and the terminal 35.
  • Container 30 The container 30 has a substantially cylindrical shape with the rotation axis RA of the motor 40 as a central axis.
  • the inside of the container is kept confidential.
  • the low-stage compressor 21 maintains an intermediate pressure
  • the high-stage compressor 23 maintains a high pressure.
  • the lower part inside the container 30 is an oil reservoir (not shown) for storing oil (lubricating oil).
  • the container 30 houses the motor 40, the crankshaft 60, and the compression unit 50 inside.
  • a terminal 35 is arranged above the container 30.
  • the container 30 is connected with refrigerant suction pipes 14a and 14b and a discharge pipe 15a, an oil return pipe 31, and an oil discharge pipe 32.
  • the discharge pipe 15a is connected to the intermediate-pressure refrigerant pipe 15.
  • the motor 40 is a brushless DC motor.
  • the motor 40 generates power for rotating the crankshaft 60 about the rotation axis RA.
  • the motor 40 is disposed above the compression unit 50 in the space inside the container 30 and below the upper space.
  • the motor 40 has a stator 41 and a rotor 42.
  • Stator 41 is fixed to the inner wall of container 30.
  • the rotor 42 rotates by interacting magnetically with the stator 41.
  • the stator 41 has a stator core 46 and an insulator 47.
  • Stator core 46 is made of steel.
  • the insulator 47 is made of resin. The insulator 47 is disposed above and below the stator core 46, and is wound.
  • crankshaft 60 transmits the power of the motor 40 to the compression section 50.
  • the crankshaft 60 has a main shaft portion 61, a first eccentric portion 62a, and a second eccentric portion 62b.
  • the main shaft portion 61 is a portion that is concentric with the rotation axis RA.
  • the main shaft 61 is fixed to the rotor 42.
  • the first eccentric portion 62a and the second eccentric portion 62b are eccentric with respect to the rotation axis RA.
  • the shape of the first eccentric portion 62a and the shape of the second eccentric portion 62b are symmetric with respect to the rotation axis RA.
  • an oil tube 69 is provided at the lower end of the crankshaft 60.
  • the oil tube 69 pumps up oil (lubricating oil) from the oil reservoir.
  • the pumped lubricating oil rises in an oil passage inside the crankshaft 60 and is supplied to a sliding portion of the compression unit 50.
  • the compression unit 50 is a two-cylinder compression mechanism.
  • the compression section 50 includes a first cylinder 51, a first piston 56, a second cylinder 52, a second piston 66, a front head 53, a middle plate 54, a rear head 55, and front mufflers 58a and 58b.
  • a first compression chamber 71 and a second compression chamber 72 are formed in the compression section 50.
  • the first and second compression chambers are spaces in which a refrigerant is supplied and compressed.
  • the first cylinder 51 is provided with a suction hole 14e, a discharge recess 59, a bush accommodation hole 57a, and a blade moving hole 57b.
  • the first cylinder 51 houses the main shaft 61 of the crankshaft 60, the first eccentric portion 62a, and the first piston 56.
  • the suction hole 14e allows the first compression chamber 71 to communicate with the inside of the suction pipe 14a.
  • a pair of bushes 56c is accommodated in the bush accommodation hole 57a.
  • the first piston 56 has an annular portion 56a and a blade 56b.
  • the first piston 56 is a swing piston.
  • the first eccentric portion 62a of the crankshaft 60 is fitted into the annular portion 56a.
  • the blade 56b is sandwiched between a pair of bushes 56c.
  • the first piston 56 divides the first compression chamber 71 into two.
  • One is a low-pressure chamber 71a communicating with the suction hole 14e.
  • the other is a high-pressure chamber 71b communicating with the discharge recess 59.
  • the annular portion 56a revolves clockwise, the volume of the high-pressure chamber 71b decreases, and the refrigerant in the high-pressure chamber 71b is compressed.
  • the tip of the blade 56b reciprocates between the blade moving hole 57b and the bush accommodating hole 57a.
  • Front mufflers 58a and 58b are fixed to the front head 53.
  • the front muffler reduces noise when the refrigerant is discharged.
  • the refrigerant compressed in the first compression chamber 71 is discharged to the first front muffler space 58e between the front muffler 58a and the front head 53 via the discharge recess 59. After the refrigerant further moves to the second front muffler space 58f between the two front mufflers 58a and 58b, the refrigerant is discharged from the discharge holes 58c and 58d (see FIG. 4) provided in the front muffler 58b under the motor 40. Is blown out into the space.
  • the compressed refrigerant discharged from the discharge holes 58c and 58d of the front muffler 58a moves to the upper space of the container 30 from the gap of the motor 40, is discharged from the discharge pipe 15a, and travels toward the high-stage compressor 23.
  • the second compression chamber 72 includes a second cylinder 52, a second piston 66, a rear head 55, a middle This is a space surrounded by the plate 54.
  • the flow of the refrigerant compressed in the second compression chamber 72 is also substantially the same as the flow of the refrigerant compressed in the first compression chamber 71, and a detailed description thereof will be omitted.
  • the refrigerant compressed in the second compression chamber 72 the refrigerant is once sent to the rear muffler space 55a provided in the rear head 55, and further sent to the front muffler spaces 58e and 58f by the front mufflers 58a and 58b. What is different.
  • the oil return pipe 31 is located below the motor 40 and in a space above the compression section 50, as shown in FIG. , Are connected to the container 30 so that the internal flow paths communicate with each other.
  • the oil blown out from the oil return pipe 31 into the container 30 collides with the insulator 47 of the motor 40, and then falls on the front muffler 58b and the annular member 53a for fixing the front head 53. Merge with the oil pool at the lower part of the inside of 30.
  • the oil return pipe 31 It is preferable to connect the oil return pipe 31 to a space above the second compression chamber 72. If the oil return pipe 31 is connected to a space lower than the second compression chamber 72, the possibility that the oil return pipe 31 will be lower than the oil level of the oil reservoir increases, and if so, forming is not preferable.
  • the oil return pipe 31 may be connected to a higher part of the container 30.
  • it may be connected to a core cut portion of the stator 41 of the motor 40.
  • it is preferable to be connected to the lower part as close as possible to the oil reservoir, because the oil is supplied to the sliding parts (in the vicinity of the compression chambers 71 and 72) earlier.
  • the inner diameter of the oil return pipe 31 is, for example, not less than 10 mm and not more than 12 mm.
  • the oil discharge pipe 32 is connected to the container 30 so that the internal flow path communicates with the space above the compression unit 50 below the motor 40.
  • connection position of the oil discharge pipe 32 to the container 30 is lower than the compression chamber 72, the oil may be excessively lost from the oil pool.
  • the position is higher than the motor 40, the difference from the discharge pipe 15a becomes small, and the significance of providing the oil discharge pipe 32 is lost.
  • the mounting height position of the oil discharge pipe 32 to the container 30 is equal to the mounting height position of the oil return pipe 31 to the container 30. This facilitates adjustment of the oil level of the oil reservoir.
  • the mounting position of the oil discharge pipe 32 to the planar container 30 is a position opposite to the discharge holes 58c and 58d of the front muffler 58b with respect to the rotation axis RA of the motor 40.
  • the opposite position means a range of 180 ° other than a total of 180 °, which is 90 ° left and right with respect to the rotation axis RA from the connection position of the oil discharge pipe 32.
  • a part of the discharge hole 58c is not at the opposite position, but here, half or more of the area of the discharge holes 58c and 58d means the opposite side.
  • the inner diameter of the oil discharge pipe 32 is equal to the inner diameter of the oil return pipe 31.
  • a pipe smaller than the inner diameter of the discharge pipe 15a is used. More specifically, the inner diameter of the oil discharge pipe 32 is, for example, 10 mm or more and 12 mm or less.
  • connection position of the oil discharge pipe 32 to the container 30 is different from that of the oil return pipe 31 to the container 30.
  • the position is 90 ° or more away from the connection position in the rotation direction of the motor 40 (the direction of the arrow in FIG. 5).
  • the position is 180 ° or more apart. In the present embodiment, this angle is represented by ⁇ .
  • ⁇ is 270 ° or more.
  • ⁇ should be 330 ° or less.
  • a first accumulator 22 is arranged upstream of a low-stage compressor 21, and a second accumulator 24 is arranged upstream of a high-stage compressor 23.
  • the accumulators 22, 24 store the flowing refrigerant once, prevent the liquid refrigerant from flowing to the compressor, and prevent liquid compression of the compressor. Since the configurations of the first accumulator 22 and the second accumulator 24 are almost the same, the first accumulator 22 will be described with reference to FIG.
  • the low-pressure gas refrigerant heated by the evaporator flows through the refrigerant pipe 13 via the four-way switching valve 5 and is introduced into the accumulator 22.
  • the gas refrigerant is introduced into the first and second compression chambers 71 and 72 from the suction pipes 14a and 14b of the compressor 21.
  • Liquid refrigerant and oil accumulate below the inside of the accumulator.
  • Small holes 14c and 14d are formed in the suction pipes 14a and 14b below the accumulator.
  • the diameter of the holes 14c and 14d is, for example, 1 mm to 2 mm.
  • the oil joins with the gas refrigerant through the holes 14c and 14d little by little together with the liquid refrigerant and is sent to the compression chamber.
  • shrink-fitting has been used for assembling a motor into a compressor.
  • the motor 40 is inserted from under the container, and is fixed to the container by a welding method.
  • a tag (TAG) welding method is used as the welding method.
  • the tag welding method refers to a method of performing spot welding at several places (for tag welding of a container and a motor, see, for example, Japanese Patent No. 5375534).
  • the multi-stage compression system 20 of the present embodiment is a system having a low-stage compressor 21 and a high-stage compressor 23.
  • This system is characterized by having an oil return pipe 31 and an oil discharge pipe 32 connected to the container 30 of the low-stage compressor 21.
  • the oil return pipe 31 returns the oil discharged from the high-stage compressor 23 to the low-stage compressor 21.
  • the oil discharge pipe 32 discharges excess oil of the low-stage compressor 21.
  • the response of the oil return pipe 31 is fast because the oil return pipe 31 is directly connected to the container 30 of the low-stage compressor 21. That is, oil can be supplied to the container more quickly than in the conventional case where the oil is connected to the suction pipe (the refrigerant pipe 13) of the first accumulator 22. Further, since the oil discharge pipe 32 is also connected to the same container 30, it is possible to quickly discharge excess oil from the low-stage compressor 21. That is, by connecting both the oil return pipe 31 and the oil discharge pipe 32 with good response to the container 30, quick control of the oil amount of the low-stage compressor 21 can be realized.
  • the oil return pipe 31 and the oil discharge pipe 32 are connected to the container 30 above the compression section 50 and below the motor 40.
  • the compression section 50 is more specifically a compression chamber.
  • the low-stage compressor 21 is a two-cylinder type compressor, and has two compression chambers, a first compression chamber 71 and a second compression chamber 72. In such a case, the term “compression chamber” refers to the second compression chamber 72.
  • the oil return pipe 31 is connected to the container 30 so that oil is supplied to the space between the motor 40 and the compression section 50.
  • the oil return pipe 31 is connected to the space between the motor 40 and the compression unit 50 so that oil is supplied. Can be supplied with oil. Further, since the oil discharge pipe 32 is connected to a position above the compression section 50 of the container 30 and below the motor 40, excess oil of the low-stage compressor 21 is discharged from the low-stage compressor without excess or shortage. can do. For this reason, the control of the oil amount of the low-stage compressor can be performed more quickly.
  • the height of the connection position of the oil return pipe 31 to the container 30 is equal to the height of the connection position of the oil discharge pipe 32 to the container 30.
  • the oil level of the oil reservoir of the low-stage compressor 21 is suppressed so as not to rise too much, and the oil amount of the low-stage compressor 21 is appropriately controlled.
  • connection position of the oil discharge pipe 32 to the container 30 is separated from the connection position of the oil return pipe 31 to the container by 90 ° or more in the rotation direction of the motor. Position. More preferably, the position is 180 ° or more.
  • the oil discharged from the container 30 can be reduced by the oil discharge pipe 32 as it is, and the amount of oil in the low-stage compressor can be appropriately controlled.
  • the compression section 50 of the low-stage compressor 21 of the multi-stage compression system 20 of the present embodiment has a muffler 58b.
  • the muffler 58b discharges the refrigerant compressed in the compression chambers 71 and 72 into the container 30.
  • the muffler 58b has ejection holes 58c and 58d.
  • the connection position of the oil discharge pipe 32 to the container 30 is a position opposite to the discharge holes 58c and 58d of the muffler 58b with respect to the rotation axis RA of the motor 40.
  • the opposite position means a range of 180 ° other than a total of 180 °, which is 90 ° left and right with respect to the rotation axis RA from the connection position of the oil discharge pipe 32.
  • the connection position of the oil discharge pipe 32 to the container 30 is far from the positions of the discharge holes 58c and 58d of the muffler 58b, the oil is discharged from the discharge holes 58c and 58d of the muffler 58b.
  • the discharge of the refrigerant from the low-stage compressor 21 through the direct oil discharge pipe 32 can be reduced.
  • the inner diameter of the oil discharge pipe 32 is equal to the inner diameter of the oil return pipe 31.
  • the oil discharge pipe 32 and the oil return pipe 31 have the same inner diameter, so that the oil return amount and the oil discharge amount are easily adjusted equally, and the oil amount of the low-stage compressor is reduced. Adjustment is easy.
  • the refrigerant is mainly a carbon dioxide refrigerant
  • the oil is an oil incompatible with the carbon dioxide.
  • oils incompatible with carbon dioxide are PAG (polyalkylene glycols) and POE (polyol esters).
  • the oil separator the oil is easily separated, and only the oil is easily returned to the low-stage compressor 21. Further, also in the low-stage compressor 21, the liquid refrigerant is easily collected upward in the oil reservoir, and the excess liquid refrigerant is easily discharged from the oil discharge pipe 32.
  • the height of the oil level of the oil reservoir of the low-stage compressor 21 is suppressed lower than in the multi-stage compression system 20 of the first embodiment.
  • the amount of oil in the low-stage compressor 21 is controlled to be smaller than that of the first embodiment and appropriately.
  • the multistage compression system 20 of Modification 1A also has the same features (4-1) to (4-7) as the multistage compression system 20 of the first embodiment.
  • one of the low-stage compressor 21 and the high-stage compressor 23 is a one-cylinder type and the other is a two-cylinder type, the same features as in the first embodiment are provided.
  • the multistage compression system 20 of Modification 1C also has the same features (4-1) to (4-7) as the multistage compression system 20 of the first embodiment.
  • the oil flowing through the oil return pipe 31 is different from the oil flowing through the oil separator 25 of the first embodiment. Therefore, the amount of the refrigerant mixed in the water increases.
  • the oil separated from the oil separator 25 may be added to the oil discharged from the high-stage compressor 23 and returned to the container 30 of the low-stage compressor 21.
  • the multi-stage compression system of Modification Example 1D has, in addition to the configuration of the multi-stage compression system 20 of the first embodiment, a liquid level meter for measuring the amount of oil in the oil sump of the low-stage compressor 21, and an oil return pipe 31. And a control valve for controlling the flow rate of the oil flowing through the oil return pipe 31. Then, below the liquid level data measured by the liquid level meter, when the liquid level is higher than a predetermined value, the flow rate of the control valve is reduced, and when the liquid level is lower than the predetermined value, the flow rate of the control valve is reduced. Control to increase the number.
  • the multi-stage compression system according to Modification 1D includes a liquid level gauge and a control valve, and can feedback control the oil amount of the low-stage compressor 21 using the oil return pipe 31.
  • the multi-stage compression system 20 of Modification 1D also has the same features (4-1) to (4-7) as the multi-stage compression system 20 of the first embodiment.
  • the multi-stage compression system 20 has a two-stage compression system including a low-stage compressor 21 and a high-stage compressor 23.
  • the multi-stage compression system of Modification Example 1E is a four-stage compression system having four compressors.
  • the lowest stage compressor is the low stage compressor 21 of the first embodiment
  • the highest stage compressor is the high stage compressor 23 of the first embodiment
  • the discharge pipes of the three compressors correspond to the intermediate-pressure refrigerant pipe 15 of the first embodiment.
  • the multistage compression system 20 of Modification 1E also has the same features (4-1) to (4-7) as the multistage compression system 20 of the first embodiment.
  • the multi-stage compression system 20 of Modification 1E is a multi-stage compression system in which four compressors are connected in four stages. In the case of a multi-stage compression system in which three compressors are connected in three stages, the present disclosure is also effective in the case of a multi-stage compression system in which five or more compressors are connected in five or more stages.
  • the multi-stage compression system 20 of the first embodiment has an intercooler 26 upstream of the intermediate-pressure refrigerant pipe 15 connected to the discharge pipe 15a of the low-stage compressor 21 and a junction 15b of the intermediate injection pipe downstream.
  • a junction 15b of the intermediate injection pipe is provided on the upstream side of the intermediate-pressure refrigerant pipe 15, and an intercooler 26 is provided on the downstream side.
  • Other configurations are the same as those of the first embodiment.
  • the multistage compression system 20 of Modification 1F also has the same features (4-1) to (4-7) as the multistage compression system 20 of the first embodiment.
  • the multi-stage compression system 20 includes an intercooler 26 upstream of the intermediate-pressure refrigerant pipe 15 connected to the discharge pipe 15a of the low-stage compressor 21 and a junction 15b of intermediate injection downstream.
  • the intercooler 26 is provided in the intermediate-pressure refrigerant pipe 15, but not the junction 15 b of the intermediate injection pipe.
  • Modification 1G does not include the economizer heat exchanger 7.
  • Other configurations are the same as in the first embodiment.
  • the multistage compression system 20 of Modification 1G also has the same features (4-1) to (4-7) as the multistage compression system 20 of the first embodiment.
  • the present disclosure is also effective when the multi-stage compression system 20 includes only the junction portion 15b of the intermediate injection in the intermediate-pressure refrigerant pipe 15 and does not include the intercooler 26. .
  • the oil discharge pipe 32 is connected to the intermediate pressure refrigerant pipe 15 downstream of the junction 15b of the intermediate injection.
  • the oil discharge pipe 32 is connected to a portion of the intermediate-pressure refrigerant pipe 15 upstream of the intercooler 26.
  • the pressure difference between the oil discharge pipe 32 and the intermediate-pressure refrigerant pipe 15 is smaller in the case of Modification 1H than in the case of the first embodiment. Therefore, in the case of Modification 1H, the amount of oil discharge is smaller than in the case of the first embodiment. Therefore, in the modified example 1H, the oil amount of the low-stage compressor is controlled to be larger than that in the first embodiment.
  • Other configurations and features are the same as those of the first embodiment.
  • the oil discharge pipe 32 may be connected between the intercooler 26 and the junction 15b of the intermediate injection on the intermediate-pressure refrigerant pipe 15, or in the middle of the intercooler 26. Although the oil discharge amount of the oil discharge pipe 32 changes according to the connection position on the intermediate-pressure refrigerant pipe 15, other configurations and features are the same as those of the first embodiment.
  • the multi-stage compression system 20 of Modification 1I also has the same features (4-1) to (4-7) as the multi-stage compression system 20 of the first embodiment.
  • the multistage compression system 20 of Modification 1J also has the same features (4-1) to (4-7) as the multistage compression system 20 of the first embodiment.
  • the present disclosure is effective when the multi-stage compression system 20 includes only the economizer heat exchanger 7 in the upstream portion of the intermediate injection pipe 12 and does not include the receiver 6. is there.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Separation By Low-Temperature Treatments (AREA)
PCT/JP2019/037670 2018-09-28 2019-09-25 多段圧縮システム WO2020067195A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201980063044.XA CN112771322A (zh) 2018-09-28 2019-09-25 多级压缩系统
EP19866259.5A EP3835685B1 (de) 2018-09-28 2019-09-25 Mehrstufiges kompressionssystem
ES19866259T ES2939052T3 (es) 2018-09-28 2019-09-25 Sistema de compresión multietapa
US17/277,687 US11428225B2 (en) 2018-09-28 2019-09-25 Multistage compression system

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JP2018-185073 2018-09-28
JP2018185073A JP6773095B2 (ja) 2018-09-28 2018-09-28 多段圧縮システム

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EP3859233B1 (de) * 2018-09-28 2023-04-26 Daikin Industries, Ltd. Mehrstufiges kompressionssystem
JP7125637B1 (ja) 2021-03-16 2022-08-25 ダイキン工業株式会社 圧縮装置及び冷凍装置
JP2024011176A (ja) * 2022-07-14 2024-01-25 三菱重工業株式会社 圧縮機ユニット及び冷凍システム

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EP3835685A1 (de) 2021-06-16
CN112771322A (zh) 2021-05-07
EP3835685B1 (de) 2023-01-25
US20210310701A1 (en) 2021-10-07
ES2939052T3 (es) 2023-04-18
JP2020056508A (ja) 2020-04-09
EP3835685A4 (de) 2021-10-13
JP6773095B2 (ja) 2020-10-21
US11428225B2 (en) 2022-08-30

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